Crushing apparatus



May 2, 1961 R. G. OSBORNE, JR., ET AL CRUSI-IING APPARATUS 4 Sheets-Sheet 1 Filed Feb. 4, 1957 ww NW QM mw m wy mw IN V EN TORS' R. cs. OSBORNE, JR, ET AL CRUSHING APPARATUS May 2, 1961 2,982,481

Filed Feb. 4, 1957 4 Sheets-Sheet. 3

05527 0, Boy/(w INVENTORS.

I M f BY W24 Ray/14am 6. 055m; (1?.

May 2, 1961 R. G. OSBORNE, JR, ET AL 2,982,481

CRUSHING APPARATUS 4 Sheets-Sheet 4 Filed Feb. 4, 1957 BflYMO/VD G- asaoe/vs, 'cle. 08597 0. BOY/0.!

INVENTORS.

United States Patent 20 CRUSHING APPARATUS Raymond G. Osborne, In, Los Angeles, and Robert O. Boykin, Sr., Glendale, Calif., a'ssignors to Osborne Associates, Los Angeles, Calif., a partnership Filed Feb. 4, 1957, Ser. No. 638,164 22 Claims. (Cl. 241-32) This invention relates to a crushing apparatus, and more particularly to means atfording quick and rapid yielding of a movable crusher member when a relatively non-crushable, oversized object falls into the crushing apparatus, and also to means for reducing shock loads of bearing means supporting one or more of the crusher members.

The invention contemplates a novel, improved crushing apparatus provided with rapid excess load relief means for a movable crusher member readily adapted for use with various types of crushing apparatuses such as crush- I ing roll means and crushers of jaw type including both single and double toggle type. The present application is a continuation-in-part of application Serial No. 520,- 747, filed July 8, 19 55, and now abandoned, entitled Crushing Roll Means.

Prior proposed crushing roll assemblies included a stationary anvil roll and a movable pressure roll, the latter being urged by various pressure means into selected spaced relation to the stationary roll. Prior pressure means usually included springs or springs in combination with fluid pressure means mounted on opposite sides of the pressure roll. The bearing means for the stationary roll were held rigidly in line by the roll frame, but the bearing means for the movable roll were usually each independently mounted to move horizontally independent of the bearing on the other end of the roll shaft. Thus, an uncrushable object passing between the rolls would move the nearest bearing a greater distance than the other bearing supporting the movable roll. Thus, if the bearings on the movable roll shaft were not swivel mounted, the commonly used babbitt or bronze bearing was subjected to a high degree of overload and resulting rapid deterioration of the bearing.

In general, prior proposed movable rolls yielded relatively slowly when an oversized, non-crushable article passed between. the rolls. Under such prior proposed roll constructions, bearings were subjected to relatively great shock when the movable roll was returned by pressure means to a selected spaced relation with respect to a companion stationary roll because metal shims were used to space the rolls. As a result, prior crushing rolls had several disadvantages including excessive damage to roll surfaces when an oversized article passed through the rolls, uneven pressure on bearings supporting the rolls, a short bearing life, and, where hydraulic means were employed, excessive wear on hydraulic piston and cylinder packing. 7

Prior proposed crushing apparatuses of double toggle jaw type included a fixed stationary jaw crusher member, a movable jaw crusher member pivotally hung from its upper end, and an eccentrically driven pitman for supporting the jaw crusher member through an arrangement of toggle members. In a single toggle arrangement, a single toggle plate was rockingly mounted at its opposite end edges on the jaw crusher member and the fixed frame respectively. When a non-crushable object fell between the jaw crusher members, the toggle member was non- Patented May 2, 1961 yieldable to the greatly increased pressure or shock load produced by said object, and. as a result the toggle member was broken and the machine damaged. In addition, the tremendous shock loads imposed on the jaw crusher member produced excessive bearing loads and the bearings operating position to permit an oversized object to pass between the crusher members and/or to permit relief of the shock load. The invention contemplates a construction of a crushing roller means whereby substantially uniform pressure 'is provided on bearing at opposite sides of the crushing roller. means. The invention further contemplates a fluid operated pressure means which exerts a pressure force in the direction of crushing movement of a crusher member and particularly along a longitudinal axis of the crushing apparatus. In the exemplary embodiments of crushing apparatuses, a pressure force is transmitted along a central longitudinal axis of movement of a movable crusher member and transmits through novel pressure-transmitting means, non-axial and unbalanced loads along an axis coaxial to a single centrally positioned pressure cylinder means to reduce wear in the cylinder means. The invention also contemplates a non-rigid pressure-transmitting connection between the movable crusher member and thefiuid operable pressure means so that lateral shock loads are not transmitted to the fiuid pressure means. 7

It is therefore among the objects of the invention to provide an improved crushing apparatus embodying a novel construction which substantially extends the life of the crushing apparatus. Y

A primary object of this invention is to disclose and provide a crushing apparatus employing fluid operated pressure means which is rapidly responsive to excessive pressure developed between crusher members to quickly release a movable crusher member from its normal op erating position.

Another object of this invention is to disclose and provide a crushing apparatus wherein shock loads imposed upon bearing means are cushioned and are reduced to a minimum. 1

Another object of this invention is to disclose and provide a novel manner of mounting movable roll means of a crushing roll means so that the bearings of the roll means are substantially uniformly loaded and held rigidly in line with the roll shaft by means of a frame means.

A still further object of this invention is to disclose and provide a fluid-operable pressure means in associa tion with a movable roll means whereby transmission of force therebetween is along a longitudinal axis of the movable roll means and fluid operable pressure means and whereby transmission of lateral forces is substan: tially eliminated.

A still further object of this invention is to disclose and provide a fluid operable pressure meansfor a'movable crusher member which includes a relatively low pressure, large cross-sectional pressure cylinder means one exemplary embodiment of this inventionapplied to a jaw type crusher apparatus, such pressure-transmitting means includes an articulatedtoggle linkgmeans, the

toggle link means including a single toggle plate which may be of usual construction and a toggle link providing a connection between the toggle plate and the fluid operaable means.

The invention also contemplat s application of the quick pressure relief means to a'jaw' crusher of double toggle arrangement and wherein shock loads imposed by an impassable non-crushable object will be relieved by fluid operable pressure means including a non-compressible fluid column and a pressure-applying fluid column superimposed thereon.

Various other objects and advantagesof this invention will be readily apparent from the following description of the drawings in which exemplary embodiments of the invention are shown.

In the drawings:

Fig. 1 is a side view, partly in. section, of a crushing roll means embodying this invention.

Fig. 2 is a horizontal sectional view taken in a transverse plane indicated by line II.II of Fig. 1.

Fig. 3 is a transverse horizontal sectional view taken in a plane indicated by line HI-III of Fig. 1.

Fig. 4 is an end view taken from the left of Fig. 1.

Fig. 5 is a transverse vertical sectional view taken in a plane indicated by line V-V of Fig. 1.

Fig. 6 is a top plan view of a crushing apparatus of double toggle jaw type modified to embody this invention.

Fig. 7 is a sectional view of the apparatus of Fig. 6, the section being taken in avertical plane passing through the longitudinal center line of the apparatus as shown by line VII-VII of Fig. 6.

Fig. 8 is a plan view of a toggle link used in the modification of Fig. 6.

Fig. 9 is a sectional view taken in a vertical plane bisecting the apparatus and embodying a modification of this invention as applied to a single toggle type jaw crushing apparatus.

Fig. 10 is a plan view of the front face of a toggle link used in the apparatus of Fig. 9.

Fig. 11 is a plan view of the opposite or back face of the link shown in Fig. 10.

A crushing apparatus embodying this invention may include various types, for example, a crushing roll means (Figs. 1 to 5), a double toggle jaw crusher means (Figs. 6 to 8), and a single toggle jaw crusher means (Figs. 9 to 11). It is understood the invention may find utility in other crushing apparatuses and this invention. is not intended to be limited to the examples shown.

The exemplary crushing roll means generally indicated at 10- (Fig. 1) includes a feed hopper 11 positioned to discharge selected pre-crushed material, such as, ore, between a stationary roll means 12 and a movable roll means 13.serving respectively as stationary crusher member and movable crusher member. The stationary and movable roll means 12 and 13 are carried by a frame means 14 and beneath the roll means may be provided a discharge hopper 15. Fluid operable pressure means are generally indicated at 16 for urging the movable roll means 13 to selected spaced relation with respect to the stationary roll means 12.

In this example, frame means 14 may include a pair of spaced parallel I-beams'18 supported and secured to any suitable surface.

The roll means 12 and 13 each include cylindrical oppositely rotatable aligned cooperable crushing members or rolls 20 and 21 respectively, which are mounted in well known manner on shafts 22 and 23 driven through gear and drive means not shown. Each crushing roll 20 and 21 may be provided with a hardened, durable, external, cylindrical surface. The construction of cylindrical rolls 20 and 21 is well known and does not form a part of this invention. 7

' Each of rolls 20 and 21 are mounted in bearing sup- .4 port or block means which may be of substantially identical construction. For purposes of brevity, only one of the bearing support means will be described in detail and like parts will be indicated with prime numbers.

Bearing support means 25, which is part of the movable roll means 13, comprises an inner upstanding end Wall 26 and an outer end Wall 27. End wall 26 is provided with a through opening 28 through which extends a portion of roll 21. End wall 27 is of somewhat heavier metal section and is provided with an internal recess 29 into which is received in spaced relation an opposite portion of roll 21. End walls 26 and 27 may be integral with diagonal side members 30, each of relatively heavy section atiord ing an inwardly and upwardly facing semicircular bearing seat at 31 for well known bearing means, such as roller bearings, for supporting ends of shaft 23. Each diagonal member 30 and end walls 26 and 27 may be integrally jointed by a reinforcing, vertically disposed web 32. A bottom horizontal side member 33 interconnects integrally web 32 and end walls 26 and 27. Bearing means seated on each bearing seat 31 may be retained by a suitable, generally semicircular bearing cap member 35 secur'd to diagonal side member 30 by a pair of bolt and nut assemblies 36. The top portions of end walls 26 and 27 may be interconnected by a flat bearing support means cover plate 37 secured thereto in suitable manner.

Each of end walls 26 and 27 are generally rectangular and may be provided with relatively thick section corners having longitudinally aligned openings 39 therethrough which include, on the movable bearing support means 13, suitable bearing sleeves of well-known construction. Aligned opening 39 is movable and stationary bearing support means 25 and 25' may receive therethrough at each side top and bottom longitudinally extending rods 40 which may have heads 41 seated against end wall 27' of the stationary bearing support means 25 and which may project beyond end wall 27 of the movable bearing support means 25 for connection to a cylinder support member 42. The four rods 40 thus slidably support the movable hearing support means 25 at a plurality of bearing areas spaced laterally and longitudinally of the rod 21.. said bearing areas b-ing sufliciently large so that nonaxial loads may be readily absorbed without damage.

The cylinder support member 42 includes a peripheral flange 43 which may be secured to I-beams 18 as by bolt and nut assemblies and which may also be secured as by bolt and nut assemblies to a top flat elongated cover member 44 extending over stationary and movable bear ing support means 25 and 25 and extending to and over cylinder support member. 42. The cylinder support member 42 also includes an inwardly directed transverse flange 45 defining a central circular opening 46 in which may be mounted a pressure cylinder member 47 of pressure means 16. The cylinder member 47 may include a radially outwardly extending annular flange 48 overlying and seated against inner margins of flange 45 for providing means to connect cylinder member 47 to flange 45 by suitable nut and bolt assemblies 49.

The rods 40 extend through aligned openings in relatively thick metal section corners of cylinder support member 42 and may be secured by pairs of locking nuts 50. Each rod 40 may be provided with a suitably finished, external cylindrical surface, and may be provided with a sliding fit in openings 39 in movable bearing support means 25 so that the bearing support means 25 may move longitudinally on rods 40 without binding. The openings 39' in the stationary bearing support means 25' may be provided with a non-sliding fit on rods 40. The stationary bearing means 25' may be secured as by nut and bolt assemblies 52 to the spaced I-beams 18. Thus the m0vable bearing support means 25 is slidably supported on four rods 40 for relative longitudinal movement above frame means 14 between support means 25 and cylinder support member 42.

' The fluid-operable pressure means 16 includes, in addition to cylinder member 47, a piston member 55 having an end wall 56 opposite to movable roll means 13 and integral with a cylindrical wall 57 extending therefrom provided with suitable sealing means 58 slidably engaging internal cylindrical surfaces on cylinder member 47. Cylinder member 47 may be sealingly connected in any suitable manner as by flanges and nut and bolt assemblies 59 to a conduit member 60 which at its other end may be connected in suitable manner to a hollow member 62 defining an internal pressure chamber 64 provided with an air inlet 63 for maintaining apredetermined fluid pressure. Fluid used in cylinder member 47 and conduit 60 is preferably non-compressible such as an oil of preselected viscosity. In chamber 64 may be provided a fluid of compressible characteristics, such as air, for direct contact with the surface of the noncompressible fluid in conduit 60. The cross-sectional area of cylinder member 47 and conduit 60 is relatively large to permit use of a relatively low pressure (such as 100 p.s.i.) in air chamber 64 while maintaining selected pressure against movable bearing support means 25 as hereinafter described.

Means to transmit pressure between piston member 55 and movable bearing support means 25 to urge movable roll means 13 at a predetermined pressure towards the stationary roll means may comprise a circular hardened pressure plate 66 carried in a complementary circular recess 67 formed in external face 68 of end wall 56 of piston member 55. Face 68 may be planar and may lie in a transverse vertical plane spaced from wall 56 of piston member 55. Contacting planar face 68 at a point virtually on the axis of piston member 55 and on the iongitudinal axis of movement of bearing support means 25 may be a pressure plate 70 having a convex external face 71 of suitable selected radius. Pressure plate 70 may be mounted in a circular recess 72 provided in a pressurecircular follower member 73. Follower member 73 may be carried in a circular enlarged recess 74 defined by rearwardly extending circumferential margins of a circular cushioning member 75. Cushioning member 75 may be carried within an annular outwardly directed rib 76 provided at an outer smaller end of a frusto-conical portion 377 formed on end wall 27 of bearing support means 25.

Cushioning member 75 may be made of any suitable resilient, yieldable material such as rubber, rubber composition or synthetic resilient materials and may be provided with a plurality of suitably spaced perforations 79. Perforations 79 are of a selected number and size to permit limited flow of resilient material thereinto when cushioning member 75 is under greater than a predetermined compression between fluid-pressure means 16 and movable roll means 13. Cushioning member 75 will become solid at a predetermined load, slightly greater than normal operating pressures.

' Enclosing the outer end of cylinder member 47 and the annular rib 76 may be a suitable, flexible, extensible and .collapsible cylindrical dust cover sleeve 80, said dust Hoover sleeve being secured in any suitable manner as by (clamping rings and serving to prevent accumulation of dust and foreign matter between the pressure-contacting plates 70 and 66.

' Between opposed and adjacent end walls 26' and 26 of the stationary and movable bearing support means 25' and 2 v2.5 and at each side thereof may be provided a plurality .of selected vertically disposed metal shims generally indicated at 82 for selectively spacing the external cylindrical elongated, rectangular plates of diiferentthickness, each -provided with an open-ended vertical slot 83 therein to permit reception of apair of vertically spaced shim mounting bolts 84. The shim mounting bolts 84 may be; threaded in end wall 26 of stationary bearing support means 25' and may extend into aligned bores 85 in 1op-' posing end wall 26 of movable bearing support meansZS to permit relative movement therebetween.

The face of end wall 26' at each side may carry an" elongated, rectangular, vertically disposed, channel-likemember 87 within which is held and confined a resilient cushioning member or pad 88. A follower plate 89 is partially received within longitudinal flanges 90 of chan-. nel-like member 87 and provides a planar face for abutment with an adjacent shim. Resilient cushioning member 88 is provided with enlarged, vertically spaced ports 91 for reception of shim supporting bolts 84. The cush of the roll faces so that said roll faces will not contact.

Adjacent to meeting surfaces of rolls 20 and 21, suitable side plates 93 may be provided to confine material being crushed to space between the rolls. Such side plates may be secured by suitable screw means 94 to end walls 26' of stationary bearing support means 25'.

Side plates 93 extend over a portion of end wall 26. of

movable bearing support means as best shown in Fig. 2. Other side plates 95 and 96 protect the bearing means upon which the shafts 22 and 23 are mounted and may be secured to hearing support means 25 and 25' in any well known manner.

In operation of the crushing roll means of this in vention, it will be understood that stationary roll means 12 is fixed to the frame 18 and roll 20 serves as an anvil roll (or stationary crusher member). Roll 21 (for movable crusher member) is spaced from roll 20 a selected distance as determined by shim means 82. The roll 21 is held in this position under a selected pressure transmitted from fluid-operable pressure means 16 and in normal operation will be substantially unyielding. For

example, an air pressure of one-hundred p.s.i. maybe maintained in pressure chamber 64, said pressure being transmitted through oil in cylinder member 47 to the piston member 55 and to the movable roll means 13 through a virtually point contact along the axis of the. cylinder and longitudinal axis of movement of roll means a 13 as provided by convex pressure plate 70. In normal operation, a precrushed material fed through hopper 11 and introduced between rolls 20 and 21 will be crushed to aselected size. I

When an oversized particle or a piece of trampiron,"

which is greater than the space provided between meeting surfaces of rolls 20 and 21, falls between the rolls,

the movable roll 12 must rapidly and quickly yield to. i

prevent damage to the rolls and to the bearings support ing said rolls.

out damage. Longitudinal movement of bearing support means 25 on four rods 40 is substantially uniform and without non-axial alignment because of the pluralityof laterally and longitudinally spaced bearing areas and because of pressure transmission along longitudinal axes of the cylinder member 47 and the movable roll means. i

the cross-sectional area of the cylinder member 47 and.

conduit 60 are relatively great, this yielding movement The relatively large diameter low pressure fluid-pressure means allows the movable roll means to rapidly move away from the stationary roll so as to pass the oversized article through the roll means with may be very rapid. For example, displacement of one inch of non-compressible fluid in a cylinder eleven inches in diameter through a conduit seven inches in diameter against a relatively large volume of compressible fluid increases pressure of the latter fluid only a small percentage.

When the article has passed between the rolls, the additional energy stored in pressure chamber 64 acts to return the movable roll means to its original spaced relation. Movement of movable bearing support means 25 towards the stationary bearing support means 25 involves a relatively large heavy mass and as the end walls 26 and shim means 84 return to normal relation, 2. large shock force is transmitted to the stationary bearing support means 25'. This shock force is substantially cushioned by limited compression of resilient side pads 88. Return of roll 21 is cushioned and forces acting upon the bearing means which support shaft 23 are substantially reduced. Bearing life has been substantially doubled in an exemplary crushing roll means embodying this invention.

It should also be noted that when an oversized article falls between rolls and 21 adjacent to one of the edges of the rolls and not centrally thereof, a nonaxially aligned pressure force is exerted against roll 21 which tends to cock axle 23 out of proper alignment with the bearing means carried by the movable bearing support means 25. Such out of alignment tendency is restrained by the four rods 40 which slidably support the movable bearing support means at a plurality of laterally and longitudinally spaced bearing areas. Since this supporting arrangement provides extensive bearing areas, the loading on said bearing areas is relatively small and wear on the bearing means is substantially reduced. Such a non-axial force is thus transmitted by the movable bearing support means 25 along the axis of movement thereof and the axis of the fluid-operable pressure means where it is absorbed. The cushioning effect of resilient member 75 serves to assist in redistribution of the load forces so that bearings on opposite sides of roll 21 are continuously subjected to a uniform loading.

It will thus be understood by those skilled in the art that the novel manner of mounting the movable bearing support means on a plurality of longitudinally extending rods and the transmission of forces coaxial to the axis of the fluid-operable pressure means of relatively large cross-sectional area affords quick release and movement of the movable roll or crusher means away from the stationary roll or crusher means. The rigid stationary bearing means, the rods 46, and the rigid stationary cylinder support member 42, all interconnected, form a cage frame or solid yoke means for the movable bearing means whereby the roll shafts are positioned at 90 to their hearing supports and bearings. The movable bearing means has slight freedom of lateral movement due to the sliding fit on the four rods 40. Such freedom and lateral movement is not detrimental to the fluid-operated pressure means because the hardened convex surfaces 71 may laterally slide on the hardened planar surface 68, it being understood that said surfaces may be lubricated. Thus, lateral forces due to a large noncrushable object passing between stationary and movable rolls at one side thereof are not transmitted to the cylinder and piston. Thus, the fluid pressure means is not subjected to sudden lateral shocks which would cause excessive wear on the hydraulic piston and cylinder packing.

Modifications of this invention shown in Figs. 6 to 8, inclusive, and 9 to 10, inclusive, show application of the present invention to crushing apparatuses of jaw type including double toggle (Fig. 7), and single toggle (Fig. 9).

Generally speaking, a crushing apparatus of double toggle type indicated at 110 may comprise a frame means .111 rigidly and fixedly supporting a stationary crusher member 112. Opposite. jaw member 112 a movable jaw crusher member 113, may be swingably mounted from the frame and oscillator or drive means generally indicated at 114, are cooperably connected through a toggle plate 115 to the movable jaw member 113. The oscillator means 114 may also be cooperably connected to an articulated toggle means generally indicated at 116 against which a selected pressure is applied by means of fluid operable pressure means 117 of a type similar to that of the first embodiment of this invention. The jaw crusher apparatus generally mentioned above is of well known construction and does not form part of this invention except for the coopcrable arrangement of the articulated toggle means 116 and fluid pressure means 117.

The frame means 111 may comprise a suitable rigid reinforced frame structure anchored to a supporting structure. The frame means 111 may be provided with a reinforced end wall 120 serving as a rigid support for stationary jaw crusher member 112 which may be secured thereto in any well known manner. The jaw member 112 includes a crusher face 121 of selected configuration and of hardened metal. The movable jaw member 113 may be swingably mounted from the frame means 111 by a transversely extending shaft 122 which may be mounted in suitable. bearings at opposite ends on frame means 111. The jaw member 113 is of rigid reinforced construction and provides a front crushing face 123 opposite face 121 and disposed in converging relation therewith so that the lower portion of said faces 121, 123 may be spaced apart a predetermined distance depending upon the size of crushed material desired. The lower portion of jaw member 113 may be pivotally connected at 124 to one end of a tension rod 125 which carries at its opposite end a compression spring 126. One end of spring 126 may be seated against an adjustable nut 127 on rod 125 and the other end of said spring may be seated against a depending bracket 128 carried by frame means 111 and ported to permit rod 125 to slidably pass therethrough.

Oscillating or drive means 114 for causing the jaw member 113 to oscillate about shaft 122 may comprise a shaft 130 mounted in suitable bearings carried by the frame means 111. One end of shaft 130 may carry an enlarged flywheel 131 and the other end may be connected to drive pulley means. Between ends of shaft 130 a pitman 132 is carried in eccentric relation thereto so that as 130 is rotated, the pitman 132 is oscillated to impart not only a reciprocal swinging motion component to the bottom end of the pitman but also a vertical motion component.

Interconnecting jaw member 113 and the lower portion of the pitman 132 is toggle plate 115 of rigid reinforced construction. Toggle plate 115 is provided a transverse elongated rockable connection at 134 with the lower portion of the back face of jaw member 113. The opposite end of toggle plate 115 is provided a rockable connection as at 135 with an adjacent portion of the pitman 132. The seats for said rockable connections 134 and 135 may comprise hardened insert elements in well known manner.

This invention is particularly directed to the construction and operation of the articulated toggle means 116 and the manner in which pressure is transmitted therethrough from the fluid operable means 117 to provide a quick release means for relieving the jaw members of excessive loading, said toggle means 116 and fluid operable means 117 being generally substituted for a fixed stationary toggle block used in prior jaw crushers of this type. In this example, toggle means 116 may comprise a toggle plate 137 of rigid reinforced construction similar to toggle plate 115. "One end of toggle plate 137 may be provided with a rockable connection at 138 to the side of pitman 132 opposite the rockable connection 135. Th oppo t end fft ss plate 1 y e p o d d a 9 rockable connection at 139 with an upstanding toggle lever or link 140, said rockable connection 139 extending transversely of the apparatus for the'approximate width of rockable connections 134, 135 and 138. Toggle link 140 may comprise a plate-like member 142 having adjacent its bottom edge a suitable transverse rockable fulcrum connection 143 to a fixed portion 144 of frame means 111. The plate-like member 142 above rockable connection 139 may symmetrically taper to a reduced top portion 145, said top portion 145 having a thickened metal section 146 projecting rearwardly in the form of a circular boss.

In this example, a rearwardly directed face 147 of boss 146 may lie in a plane transverse to the longitudinal axis of the apparatus and provide pressure-transmitting contact with a convex or dome-shaped face 148 provided on the external end of a sleeve type piston 149 of fluid operable pressure means 117. The axis of piston 149 is coaxially aligned with the axis of circular boss 146 so that dome contoured face 148 provides at said axis virtually a point pressure contact with toggle link 140. The axes of the piston 149, boss 146, toggle link 140 all lie in a vertical plane which passes through the longitudinal axis of the crushing apparatus. While this arrangement of a simple point pressure contact is exemplarily shown in this embodiment, it is understood that the pressuretransmitting means, that is, a cushioning member 75, pressure plate 70 with convex face 71, and a pressure disturbing follower member 73, between the piston and the movable crushing roll of the prior embodiment may be used. Toggle link 140 provides through rockable connections 143 and 139 a lever of the second class for forces applied to it through piston 149.

The fluid operable pressure means 117 includes in addition to piston 149 a generally horizontally disposed cylinder means 150 of a size and construction similar to that of the prior embodiment, said cylinder means being rigidly supported from frame means 111. The cylinder means 150 is curved upwardly at its rear portion and may be partially filled with a virtually non-compressible fluid 151 such as a suitable oil. Above the surface 152 of the oil is provided a chamber 153 which may be filled with a compressible inert fluid 154 such as air or gas,

said compressible fluid being maintained under a preselected pressure by well known suitable means including a compressed air source (not shown) such as described in the prior embodiment.

Means to precisely position the movable jaw crusher member 113 in desired relation to the stationary jaw member llz may comprise a frame portion 156 which extends transversely forwardly of toggle link 140 and which may be provided with a contact face 157 for abutting engagement with a finished surface portion 158 on the front face of toggle link 140. Means may be provided for positioning shims of varying thickness at face 157 in well known manner. In normal operating position the surface 158 of toggle link 140 is in pressure contact with face 157 of the frame. The toggle plates 115 and 137 are held in assembly with the pitman 132,

jaw member 113, and toggle link 140 by the tension rod 125 and spring 126 which biases the jaw member rearwardly and by the fluid operable pressure means which presses the toggle link 140 forwardly against the frame portion 156. n

In operation, actuation of oscillating means 114 will cause pitman 132 to liinitedly swing backwards and forwards with a limited up and down motion produced by the eccentric mounting so as to transmit through toggle' plate 115 such motionto jaw crusher member 113 to crush' material introduced between jaw crusher members 113 and 112. In normal operation toggle plate 137 follows the motion of the pitman 132 and the operable pressure means retains toggle link 140 against frame portion15 6. The rockable connection 139 is immovable posed by the oscillatory motion of the pitman 132 by reg 10 and the operation of the double toggle link crushers.

Under conditions of momentary shock loading, as

apparatus is similar to sitar;

when a virtually non-crushable object is received tween the jaw members, but is capable of passing therethrough, such shock loading is transmitted rearwardly to toggle link 140. When the magnitude of the. shock] force exceeds that pressure effectively acting on the second class lever toggle link 140 by the fluid operable pressure means, the link 140 will pivot about rockable fulcrum connection 143, pressure face 158 will disengage face 157 on the frame portion 156, and the piston 149 will move rearwardly against the non-compressible fluid column and compress the compressible fluid column in cushion chamber 153. The large diameter of the cylinder and its area of communication with the compressible fluid column permits immediate response of the piston to such shock loads as in the prior embodiment. The toggle plates and 137 will be retained in assembly by spring 126 on rod which biases the movable jaw member rearwardly. Since the shock load is immediately relieved, excessive loads on bearings supporting shafts 122 and are avoided and damage to said bearings is virtually obviated. As the momentary shock load passes due to movement of the movable jaw member, the fluid pressure means 117 restores toggle link to normal operating position in pressure contact with face 157 on frame portion 156 and the movable jaw member 113 is again in normal preselected operating position.

Under conditions of permanent excessive shock loading, as when a non-crushable impassable object is received. between the jaw members, action of the quick releasev means is quite similar as above described in the response .1 of the toggle link 140 and fluid pressure means 117.. However, as the impassable object moves into fixed per manent lodged position between the jaw members, it will: be apparent that relative motion between the jaw members must cease. Under such conditions the oscillatory motion of the pitman is now transmitted rearwardly through toggle plate 137, toggle link 140, to pisto1r 149. The rockable connection at 134 now becomes irr effect a fixed non-movable support. Since the piston is: of large diameter and communication between the noncompressible fluid and compressible fluid is over a relatively large area, the piston now absorbs the loads imciprocal movement in the cylinder means. This resilient reciprocal cushioning response of the piston thus limits the shock or excessive loads imposed upon the jaw members and the toggle plates with the result that break-v age of toggle plates and damage to bearings is virtually' eliminated.

It will thus be understood by those skilled in the art plied to the movable jaw crusher member 113. In abnormal operating conditions the rockable connection 139' is not immovable but may yield in accordance with the differential of pressure forces transmitted from the jaw crusher member 113 and from the selectively loaded fluid operable pressure means.

134 becomes immovable and the drive forces are now transmitted through the movable connection 139 to be absorbed by the fluid pressure means.

does'form a part of this invention and for brevity Under the extreme .con-, 3' dition of an impassable object the rockable connection" In the embodiment of this invention shown in Figs. 9 to ll inclusive, the invention is applied to a jaw type crushing apparatus of single toggle type. As in the em bodiment described in Figs. 6 to 8, inclusive, the general;v construction of the crushing apparatus is well known and aesaissr notbe described in detail. Thusythe rigid frame means 170 which carries the stationary vertically disposed jaw member 171 in operable relation to a movable jaw crusher member 172 may be of suitable well known construction. The movable jaw crusher member 172 in this embodiment is eccentrically mounted about a shaft 173 supported in suitable bearings from frame 170, said shaft carrying a flywheel 174 at an end thereof. The lower end of jaw member 172 may be pivotally connected at 175 to a tension rod 176 biased by a coil spring 177, sleeved thereover and seated between a nut spring seat 178 carried by rod 176 and a depending spring seat bracket 179 carried by a portion of the frame means 170. The jaw crusher member 172 is provided with a suitable crushing face 181 and on its back side may be provided with a rockable connection at 182 to a trans versely disposed rigid reinforced toggle plate 183. All of this construction is well known in the. art.

In this embodiment a toggle lever or link 185 may be disposed with its neutral axis slightly inclined to the plane of toggle plate 183. Toggle link 185 may be of rigid reinforced castable construction of relatively thick metal section and may include well known means providing a transversely extending concave in section groove affording a transverse rockable connection at 186 to the end of toggle plate 18 opposite connection 182. Below said rockable connection 186 and slightly rearwardly thereof toggle link 185 may be provided with a rockable support and fulcrum connection 188 to a transversely extending member 189 seated on a bottom frame portion 190 of frame means 170. Above fulcrum connection 186, toggle link 185 may be provided with a finished surface 191 normally positioned in pressure contact with face 192a of an intermediate portion 192 of the frame means. The toggle link 185 extends beyond surface 191 and symmetrically tapers to a top reduced end 193 which may be provided With a bolt assembly carrying at one end a ball or partially spherical member 194 cooperable with a corresponding spherical recess or socket 195 provided on the end of a relatively large diameter piston 196 of fluid operable pressure means generally indicated at 197. The axis of the ball and socket connection is perpendicular to the longitudinal axis of the toggle link and lies in a vertical plane passing through the longitudinal axis of the crushing apparatus.

The fluid operable pressure means 197 includes in addition to the piston 196 a cylinder means 198 disposed with its axis coaxial to the axis of the ball and socket connection. The cylinder means 197 may be supported at its lower end from a fixed frame portion 198 by means of a ball and socket connection 199. The cylinder means 197 is thus mounted at opposite ends of its axis on ball and socket connections which in effect serve as universal connections.

The cylinder means 197 may be filled with a virtually noncompressible fluid such as a silicone oil and an. enlarged generally semi-circular transversely elongated opening 201 may be provided adjacent its bottom end for fluid communication over a large flow area with a cylinder means 202 having a transversely elongated neck 202:: which may contain a suitable compressible fluid such as gas or air. The compressible fluid in cylinder means 202 may be maintained under preselected pressure from a suitable supply source (not shown).

The assembly of the fluid operable pressure means 197 including cylinders 198 and 202 may be supported at its center of gravity by a suitable spring 203 carried by an overhead channel frame member 204 rigidly secured to the frame means 170. Thus, the fluid operable pressure means 197 is capable of immediate adjustment of its position between the two universal connections so that non-axial lateral forces will not be transmitted to piston 196 and to the cylinder198 so as to causeundue wear therebetween.

The operation of the jaw crushingapparatus of this.

embodiment isquitelsimilar to thatdescribed in the em.

bodiment of Figs..6 to 8 inclusive. In normal operation,

the .toggle link is seated in pressure contact against i face 192a. When a non-crushable passable object falls between the jaw members 171 and 172, the togglelink 185.. may. turn about its fulcrum connectionl88 so that the. shock load may be absorbed by the fluid operable pressure means 197; When a non-crushable impassable object falls between the jaw members a similar responsive action occurs in the toggle 185 and fluid operable pressure means 197 inthat the jaw member 172 becomes relatively immovable and the forces transmitted to the jaw member through the eccentric connection of the shaft 173 are transferred through the toggle plate 183, to the toggle link 185, and to the piston 196 and result in reciprocal movement of the piston 196.

In this embodiment means are provided to shut off and cease operation of the crushing apparatus and to signal an operator when an impassable object becomes fixedly lodged between thejaw members 171, 172. Such signal means may comprise a spring type switch pressure element 208 carried on the back face of toggle link 185. Opposite to element 208 may be mounted a switch means 209 having a switch button 210 adapted to be contacted and pressed by element 208 when toggle link 185 is pivoted about its fulcrum 188 when a non-passable object is lodged between the jaw members. The electric circuitry of switch means 209 and its connection to the apparatus control panel and to a signal horn is not shown because such is well known in the art. Closure of switch button 210 will cause a motor circuit to be opened to stop the motor. It will also cause another circuit to be closed to actuate a signal horn which will warn an operator that the apparatus is in trouble. It will be readily apparent that such signal means may be selectively adjustable by positioning of the switch means 209 and the spring pressure element 208 so that the apparatus will not be disturbed in its normal operation except when an impassable object is lodged in the apparatus.

In the embodiment shown in Figs. 6 to 8 and 9 to 10 inclusive, those skilled in the art will readily understand that an impassable object lodged between the jaw members may be readily and conveniently removed by reducing the pressure of the compressible fluid in the cushion chambers. Such reduction of pressure will cause the piston to be forced inwardly by the gravitational weight of the toggle links and by the spring-biasing forces acting on the articulated toggle means by the springs connected to the jaw members. Such release of pressure will cause the movable jaw member to open further and the object may either fall from between. the jaw members or it will be loosened so that it may be readily, manually removed. Upon increase in the pressure of the compressible fluid to its normal pre-selectedoperating pressure the toggle means and jaw members will be returned to normal operating position.

It will be apparent to those skilled in the art that the several embodiments of this invention have provided a i simple, effective means for quickly and immediately relieving shock loads imposed upon movable crushing members and that such immediate response to such shock loads will not only reduce the wear and damage on bear ings supporting the crushing members but will also permit the utilization of crushing forces of lesser magnitude ing the movable roll means for movement toward and' said fluid-operable pressure means includes a non-compressible fluid means and a compressible fluid means maintained under a selected pressure.

3. A crushing roll means as stated in claim 2 wherein said non-compressible fiuid means includes a piston and cylinder member of large cross-sectional area.

4. In a crushing roll means, the combination of: a frame means; a stationary roll means carried bythe frame means; a cylinder support member carried by the frame means in spaced relation to said stationary roll means; a fluid-operable pressure means carried by said cylinder support means; a movable pressure roll means between said stationary roll means and said fluid-operable pressure means; rigid means extending between said stationary roll means and said cylinder support means slidably carrying said movable roll means and maintaining said movable ro ll means virtually parallel to said stationary roll means; and resilient means at opposite sides of the movable roll means for cushioning movement of said movable roll means toward and away from said stationary roll means.

5. A crushing roll means as stated in claim 4 wherein said movable roll means includes a unitary bearing support means having a centrally disposed convexpressure plate provided with a convex face for contacting said fluid-operable pressure means at the axis thereof.

6. In a crushing roll means, the combination of: a stationary roll means; a pressure roll means mounted for slidable movement along a longitudinal axis toward and from the stationary roll means, said stationary roll means and said pressure roll means including opposed spaced end faces; means slidably mounting the pressure roll means and holding vthe pressure roll means in parallel relation to the stationary roll means and against lateral shock loads; fluid-operable pressure means coaxial to said axis and cooperable with said pressure roll means to urge said pressure roll means toward said stationary roll means; and cushioning means between said stationary and pressure roll means, said cushioning means including resilient pads supported between said opposed end faces.

7. A crushing roll means as stated in claim 6 wherein said cushioning means includes confined resilient pads provided with a plurality of perforations.

8. In a crushing roll means, the combination of: a frame means; a stationary roll means fixed to the frame means; a movable pressure roll means; means slidably supporting the movable roll means for movement along a longitudinal axis toward and away from the stationary roll means; fluid-operable pressure means carried by the frame means and coaxially aligned with said axis; pressure contact means between the movable roll means and the fluid-operable pressure means at said axis; andpressure plates carried by said movable roll means and said fluid-operable pressure means in contact along the axis of movement of said movable roll means; and cushioning means supporting one of said pressure plates.

9. A crushing roll means as stated in claim 8, wherein said cushioning means includes a perforated resilient pad.

10. In a crushing roll means, the combination of: a frame means; a stationary roll means carried by the frame means; a cylinder support member carried by the frame means in spaced relation to said stationary roll means; a fluid-operable pressure means carried byzsaidi cylinder support means; a movable pressure roll meat! .1

between said stationary roll means and said fluid-operablef pressure means and including a pressure plate; means'exroll means; and resilient means for cushioning movement of said movable roll means toward and away from said stationary roll means; said resilient means includinga confined perforated pad of resilient material interposed? between said pressure plate and said movable roll means.

11. In a crushing roll means, the combination of: a frame means; a stationary roll means carried by the. frame means; a cylinder support member carried by the frame means in spaced relation to said stationary roll means; 'a' fluid-operable pressure means carried by said cylinder support means; a movable pressure roll means between said stationary roll means and said fluid-operable pressure means; means extending between said stationary roll. means and said cylinder support means slidably carrying said movable roll means; and resilient means for cushioning movement of said movable roll meanstoward and away from said stationary roll means; said resilient means including a pair of resilient perforated pads at each side of. said roll means and between said roll means.'

12. In a crushing roll means, the combination of: a frame means; a stationary roll means carried by the frame means; a cylinder support member carried by the frame means in spaced relation to said stationary roll means; a fluid-operable pressure means carried by said cylinder support means; a movable pressure roll means between said stationary roll means and said fluid-operable pressure means; means extending between said stationary roll means and said cylinder support means slidably carrying said movable roll means and including aplurality of longitudinally extending rods secured to said stationary roll means and said cylinder support means; and resilient means for cushioning movement of said movable roll means toward and away from said sta- I tionary roll means. i

'13. In a crushing apparatus for ore, gravel, and like} material, the combination of: a frame, means having a 1 longitudinal axis; a stationary crusher memberfixed on the frame means against movement longitudinally of the frame means;fa1 movable crusher member cooperable with the stationary crusher member and'having an axis transverse to the longitudinal axis of the frame means; means on the frame means supporting the movable crusher member for movement toward and away from Y the stationary crusher member while restraining the mov 1 able crusher member against misalignment with respect to the stationary member; fluid operable pressure means carried by the frame means and having an axis extending in the direction of movement of the movable crusher member and in a vertical plane passing through the longitudinal axis of the frame means; pressure-transmitting means between the movable crusher member and the fluid-operable pressure means and including laterally free pressure-contacting surfaces lying transversely of the axes of the frame means and at the axis of the fluid-operable pressure means; said fluid operable pressure means including a chamber of large cross-sectional area and hav-,

ing a piston therein providing one of said pressure contacting surfaces, said chamber having an extension provided with an area approximately that of the chamber, said chamber and extension containing a non-compres sible fluid acting against said piston, and means contain, v

14. An apparatus as stated in claim 13 wherein said pressure-transmitting means includes a toggle means inier eonnecting'in pressure-transmitting:relation through said pressure-contacting surfaces said fluid pressure means and said movable crusher member.

15. An apparatus as stated in claim .13'ineluding .a toggle plate; and said pressure-transmitting means includes a toggle lever fulcrumed on said frame meansand provided with a transversely extending rockable. connection to the toggle plate between the ends of the lever.

16. A crushing apparatus as stated in claim 15 including stop means on the frame means to position said toggle lever under normal operating conditions.

17. A crushing apparatus as stated in claim 15 including cooperable switch means on the toggle lever and on the frame means operative when an impassable object is lodged between said crusher members.

18. A crushing apparatus as stated in claim13 including a toggle plate; a toggle lever fulcrumed on the frame means andprovided with a rockable connection to one end of said toggle plate; said fluid-operable pressure means being provided with a piston; said pressure-transmitting means interconnecting for pressure transmission one end of the toggle lever and said piston, and lever stopping means on the frame means engaged by said toggle lever in normal operative position thereof.

19. A crushing apparataus as stated in claim 18 including resilient suspension means for said fluid-operable means.

20. A crushing apparatus as stated in claim 13 including a toggle plate; spring means biasing said movable crusher member against said toggle plate; a toggle lever fulcrumed on the frame means of said apparatus and yieldably connecting the fluid operable pressure means and the toggle plate, said toggle lever being retained in normal operating position against said spring means by said fluid-operable pressure means and readilyyieldable to relieve shock loads transmitted through said toggle plate by compressibility of said fluid-operable pressure means.

21. An apparatus as stated in claim 13 wherein said pressure transmitting means includes a transversely extending toggle plate cooperably associated with said movable crusher member, a vertically extending toggle link having a transversely extending rockable connection to said toggle plate intermediate ends of said link, one end ofsaid toggle link being pivotally mounted on said frame means and the other end of said toggle link having one of 16 said. pressure-contactingsurfaces for pressure-transmitting connection to said fluid-operable means.

22. A quick release means for absorbing shock load applied to a movable crusher member of a crushing apparatus comprising: means connected to the crusher member and provided with a pressure-transmitting face lying in a plane transversely intersecting the longitudinal axis of the apparatus; and fluid operable pressure means including a chamber of large cross-sectional area and an extension to said chamber having a cross-sectional area approximately that of said chamber; a piston in said chamber having an external piston face in contact with said pressure-transmitting face, said chamber and extension containing a non-compressible fluid acting against said piston under a preselected pressure force, means containing a compressible fluid in contactwith said non-compressible fluid at the end of said extension whereby said non-compressible fluid in said chamber and extension may quickly transmit pressure forces acting against said external piston face to said compressible fluid.

References Cited in the file ofthis patent UNITED STATES, PATENTS 509,730 Griffin Nov. 28, 1893 574,273 Rogers Dec. 29, 1896 667,371 Swenson Feb. 5, 1901 674,057 Edison May 14, 1901 1,010,164 Maxwell Nov. 28, 1911 1,519,657 Biggert Dec. 16, 1924 1,708,185 Mattei Apr. 9, 1929 1,730,906 Voegel Oct. 8, 1929 1,852,435 Ritchie Apr. 5, 1932 2,070,528 Evans Feb. 9, 1937 2,082,498 Kent et al. June 1, 1937 2,302,723 Symons Nov. 24, 1942 2,588,180 Traylor Mar. 4, 1952 2,620,629 Gauldie Dec. 9, 1952 2,636,690 Roubal Apr. 28, 1953 2,667,309 Becker Jan. 26, 1954 2,738,933 Dougherty Mar. 20, 1956 FOREIGN PATENTS 728,437 Germany Nov. 27, 1942 937,701 Germany Jan. 12, 1956 

